EP0780598A1 - Dämpfungsmechanismus für einen Riemenspanner - Google Patents

Dämpfungsmechanismus für einen Riemenspanner Download PDF

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Publication number
EP0780598A1
EP0780598A1 EP96308914A EP96308914A EP0780598A1 EP 0780598 A1 EP0780598 A1 EP 0780598A1 EP 96308914 A EP96308914 A EP 96308914A EP 96308914 A EP96308914 A EP 96308914A EP 0780598 A1 EP0780598 A1 EP 0780598A1
Authority
EP
European Patent Office
Prior art keywords
pivot
tensioner
arm
belt
brake shoe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96308914A
Other languages
English (en)
French (fr)
Other versions
EP0780598B1 (de
Inventor
Alexander Serkh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gates Corp
Gates Rubber Co
Original Assignee
Gates Corp
Gates Rubber Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gates Corp, Gates Rubber Co filed Critical Gates Corp
Publication of EP0780598A1 publication Critical patent/EP0780598A1/de
Application granted granted Critical
Publication of EP0780598B1 publication Critical patent/EP0780598B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H2007/084—Means for varying tension of belts, ropes, or chains with vibration damping means having vibration damping characteristics dependent on the moving direction of the tensioner

Definitions

  • the invention relates to a tensioner with a damping mechanism and a belt drive system that includes such s tensioner. More particularly, the invention relates to a tensioner with a torsional spring that biases the position of a pivot-arm to which a belt engaging pulley is rotatably mounted.
  • the tensioner of the invention with its damping mechanism is particularly useful in controlling tension of a V-ribbed belt drive system such as a front end accessory drive for automotive engine applications.
  • a mechanical tensioner is used to automatically control the tension of a V-ribbed belt of a front end accessory drive for automotive engine applications.
  • Such a tensioner has a pivot-arm that rotates about a pivot secured to a base and uses a sleeve-bushing on the pivot to provide a bearing surface for the rotating pivot-arm.
  • Many of such bushings are made of plastic and are subject to wear over the expected life of the tensioner.
  • a torsional spring is often used with one end connected to the pivot-arm and the other end interconnected through the base to bias the position of the pivot-arm and position an attached pulley against a belt.
  • the spring is also used to generate a spring force operative with a damping means that generates a normal force component to a friction sliding surface to inhibit or dampen oscillatory movements of the pivot-arm.
  • the bearing for the pulley is in the same radial plane as the bushing so that bushing loads are minimized and bushing wear does not appreciably lead to "free play” or "cocking" of the pivot-arm with attendant misalignment of the pulley over the expected operative life of the tensioner.
  • Examples of belt tensioners with the pulley bearing aligned in a common radial plane with the pivot-arm pivot bushing are disclosed in U.S. Patent Nos. 4,696,663 and 5,045,031.
  • Another belt tensioner design centralizes the location of the pivot-arm between oppositely wound torsional springs and locates the pulley bearing midway between nylon insert bushings.
  • the symmetrical design of the springs and location of the bushings result in substantial equal wear of each bushing.
  • An example of such a tensioner is disclosed at Page 8 of SAE Technical Paper Series Number 790699. Problems of such tensioners include: their bulk because of the two spring design making them unsuitable for fitting within the available space limitations; their cost because of the several number of parts associated with the two spring design; and their lack of a sophisticated damping mechanism.
  • a tensioner design that solves the bulk, cost, and damping problems of the aforementioned SAE tensioner is disclosed in U.S. Patent No. 4,473,362.
  • the '362 tensioner has a pivot-arm attached to an off-set cylindrical member that supports the pivot-arm and rotates about a pivot secured to a base. Only one torsional spring is used with one end connected to the pivot-arm and the other end connected to the base.
  • a single sleeve-type bushing on the pivot has a bearing surface that supports the cylindrical member. The radial plane of a pulley bearing is off-set in relation to the sleeve-type bushing which introduces a moment or couple as a load which must be carried by the bushing.
  • Such tensioners are sometimes referred as "Zed” type tensioners because of the off-set of the pulley relative to its support or base structure. Unequal pressure loads introduced into bearing surfaces of the bushing can result in excessive bushing wear and attendant pulley misalignment.
  • the belt of a drive system utilizing such Zed type tensioners engages the pulley and generates a belt force at the pulley which is transmitted to the cylindrical member (hereinafter hub load).
  • hub load the cylindrical member
  • the unequal loads to the bushing are reduced by a damping means that generates a normal force component acting in generally the same direction as the belt force component transmitted to the cylindrical member.
  • a tensioner is provided that is particularly useful in V-ribbed front end accessory belt drive systems used in automotive applications where pulley alignment over the expected life of the tensioner is important.
  • the belt tensioner of the invention is of the "Zed" type with a pivot-arm attached to an off-set cylindrical member that supports the pivot-arm and rotates about a pivot secured to a base.
  • a sleeve-type bushing on the pivot has a bearing surface that supports the cylindrical member.
  • a pulley is attached to the pivot-arm for engaging a belt of a belt drive system and receiving a belt load that generates a belt force component that is transmitted to the cylindrical member (hub load).
  • the hub load and normal force component generated by the damping mechanism are carried by at least one or two bushings that have two axially spaced-apart bearing surfaces.
  • the bushings have an axial length that size the bearing surfaces for an average pressure contact such that each bearing surface radially wears at substantially the same rate. The bearing surfaces wearing in at substantially the same radial rate assures pulley alignment over the expected life of the tensioner.
  • a damping mechanism where the normal force generated by the damping means is greater than the spring force activating the damping mechanism.
  • the damping means has a brake shoe with an outer arcuate surface that engages the inside of a second cylindrical member to provide friction surface sliding therewith.
  • the brake shoe has two oppositely facing inside ramp surfaces where one of the ramp surfaces slideably engages a complementary ramp surface of the base and the other ramp surface slideably engages an extension of the spring end which applies the spring force to the brake shoe. The angle between the two ramp surfaces and direction of forces are such that a normal force component transferred to the brake shoe is greater than the applied spring force.
  • Another advantage of the invention is a damping mechanism which generates a normal force greater than the spring force which can be used for secondary advantages such as increased damping.
  • a tensioner 10 with a pulley 12 is illustrated as a component part of a belt drive system that includes a belt 16 and several pulleys.
  • the belt 16 is entrained around a crank pulley 18, a fan/water pump pulley 20, a power steering pulley 22, an alternator pulley 24, an idler pulley 26, and the tensioner pulley 12.
  • the tensioner pulley 12 engages the belt 16 and is shown in several positions to schematically show how the pulley moves to adjust belt tension.
  • the tensioner pulley 12 engages the belt 16 and receives a belt load in the form of belt tension T1, T2, of adjacent belt spans 28, 30.
  • the belt tension T1, T2 combine to generate a belt force component BF along a bisector or an angle formed between the belt spans 28, 30.
  • the belt force component being axially off-set from a pivot 32 of the tensioner, generates a complicated hub load including forces and moments that are symbolically (i.e. not specifically) represented by the arrow HL.
  • the tensioner 10 is of the mechanical type and includes a base 34, a torsional spring 36, with one end 38 connected to a pivot-arm 40 and an other end 42 interconnected through the base generating a spring force operating with a damping means 44.
  • the pivot-arm 40 is attached to an off-set cylindrical member 46 that supports the pivot-arm 40 and rotates about the pivot 32.
  • Sleeve-bushings 48, 50 are preferably of the polymeric type and positioned on the pivot to support the cylindrical member with its attached pivot arm.
  • the bushings may included flanges 52, 54 as a thrust bearing for the cylindrical member and a flanged fastener such as a bolt 56 that retains the pivot-arm.
  • the pulley 12 is rotatable mounted to the pivot-arm 40 such as by means of a ball bearing 58 on a stub shaft 60 formed of the pivot-arm.
  • the bearing is retained on the stub shaft such as by means of a bolt 62.
  • Ears 64, 66 with bolt receiving holes 68, 70 may be used a means for mounting the tensioner to an engine (not shown) as part of the belt drive system.
  • a second cylindrical member 72 that is off-set from the pivot-arm and coaxial with the first cylindrical member 46 provides a housing for the torsional spring and the damping means 44.
  • the second cylindrical member extends into a cylindrical depression 74 formed in the housing in a somewhat "telescopic" fashion.
  • a dust seal 76 maintains a clean environment for the spring and damping means 44.
  • the second cylindrical member also forms part of the damping means.
  • the damping means 44 is a mechanism that includes an extension 78 of spring end 42, a brake shoe 80 with an outside arcuate friction surface 82 that engages a complementary inside surface 84 of the second cylindrical member 72.
  • the brake shoe has oppositely facing, inside ramp surfaces with a space intercept at an apex of an angle A.
  • the brake shoe has a lining 90 that defines the friction surface 82 and is attached to the shoe such as by teeth 92 that snap into slots 94 formed of the brake shoe.
  • the end of the spring 42 that interconnects through the base 34 bends around a protuberance 96 (shown as a post) formed of the base or attached to the base.
  • the extension 78 of the spring end slideably engages inside ramp surface 86 formed of the brake shoe.
  • the base includes a protuberance 100 (shown as a post) formed of the base or attached to the base and which has a complementary ramp surface 102 that slideably engages the ramp surface 88 formed of the brake shoe.
  • the spring 36 under torsion applies a spring force SF substantially normal to inside ramp surface 86 pressing inside ramp surface 88 of the shoe against the complementary ramp surface 102 of the base and pressing the lining against the complementary inside surface 84 of the second cylindrical member 72 causing a reactionary force RF to be imparted to the shoe.
  • the spring force SF applied to the inside ramp surface 86 in combination with the reactive force RF at the inside ramp surface 88 generates a normal force NF that is equal and opposite a force 104 carried at the complementary inside surface 84 of the second cylindrical member 72.
  • the so generated normal force NF is generally in the same direction (generally parallel) to the belt force BF.
  • the magnitude of the spring force can be varied by changing the angle A between the inside ramp surfaces and the direction of the spring force SF. The greater the angle, the greater the normal force.
  • the angle A between inside ramp surfaces may be from about 60 to 140°, but more preferably, angle A is from about 90 to 120°.
  • the damping means 44 may be used in tensioners using a torsional spring such as of the type disclosed in U.S. Patent No. 4,696,663 and where it is desired to increase the normal force such as for the purpose of enhanced damping.
  • the magnitude, direction, and location of the belt force and normal force of a tensioner may optionally be used to size the bearing surface of a bushing disposed on the pivot for an average pressure contact so that each bearing surface radially wears at substantially the same rate.
  • the belt force BF being off-set from the cylindrical member 46 operates to apply a clockwise moment to the cylindrical member 46 in the cross-section shown in Figure 4.
  • the normal force NF operating against the second cylindrical member operates at a moment arm 126 to move the cylindrical member in a counter clockwise direction in the plane of the cross-section of Figure 4.
  • the forces so introduced to the cylindrical member are carried by bushings 48, 50 which each has a bearing surface that supports the cylindrical surface and may be represented by a bearing force component BC1, BC2.
  • the bearing surfaces are spaced a distance D apart.
  • Bearing force component BC1 operates at a moment arm 128 relative to the belt force BF and bearing surface component BC2 operates at a moment arm 130 relative to bearing force BF.
  • each bearing 48, 50 has a bearing surface BS1, BS2 that supports a load CL1, CL2, as the pivot-arm is rotated in a clockwise direction.
  • a damping mechanism generates a force which adds to the loads carried by the bearings when the pivot-arm is moved in one direction and subtracts to the loads carried by the bearings when the pivot-arm is moved in a clockwise direction.
  • the load CL1 introduced to the bearing surface BS1 in the clockwise direction is greater than the load CL2 introduced into the bearing surface BS2 as the pivot-arm is moved in a clockwise direction.
  • the loads to the bearing surface substantially change when the pivot-arm is moved in the opposite or counter clockwise direction.
  • the load CC1 that is introduced to bearing surface BS1 is smaller than the load CC2 introduced to bearing surface BS2 when the pivot-arm is moved in a counter clockwise direction.
  • the loads CL1 and CC1 may be averaged to determine an average load that must be carried by bearing surface BS1.
  • the load CL2 and CC2 may be averaged to determine the loads that must be carried by bearing surface BS2. It is probable that the so averaged loads are unequal as illustrated in Figure 5C.
  • the average load CA1 (equal and opposite BC2) is larger than the average load CA2 (equal and opposite BC2).
  • bearing surface BS1 and BS2 have an axial length BL1, BL2 that size each bearing surface for an average pressure contact PB1, PC2 such that each bearing surface radially wears at substantially the same rate.
  • bushing 48 has a longer axial length BL1 than does bushing 50 having axial length BL2 so that the pressure contact PC1 substantially equals PC2.
  • the length of the bushings can be sized for a pressure contact that yields substantially the same radial wear rate.
  • a tensioner of the invention was constructed with a 76.2 mm diameter pulley, a 100.8 in/lbs torsional spring, and with the following characteristics:
  • the average normal force NF is greater than the average spring force which is in accordance with the feature of the invention.
EP96308914A 1995-12-18 1996-12-09 Dämpfungsmechanismus für einen Riemenspanner Expired - Lifetime EP0780598B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US573827 1995-12-18
US08/573,827 US5632697A (en) 1995-12-18 1995-12-18 Damping mechanism for a tensioner

Publications (2)

Publication Number Publication Date
EP0780598A1 true EP0780598A1 (de) 1997-06-25
EP0780598B1 EP0780598B1 (de) 2000-11-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96308914A Expired - Lifetime EP0780598B1 (de) 1995-12-18 1996-12-09 Dämpfungsmechanismus für einen Riemenspanner

Country Status (9)

Country Link
US (1) US5632697A (de)
EP (1) EP0780598B1 (de)
JP (1) JP2854292B2 (de)
KR (1) KR100208042B1 (de)
AT (1) ATE197341T1 (de)
BR (1) BR9606062A (de)
CA (1) CA2192422C (de)
DE (1) DE69610811T2 (de)
ES (1) ES2152497T3 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005047265A1 (de) * 2005-10-01 2007-04-05 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs
DE102006023565A1 (de) * 2006-05-19 2007-11-22 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen oder eine Kette
DE102007015676A1 (de) * 2007-03-31 2008-10-02 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs

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US5964674A (en) * 1997-03-21 1999-10-12 The Gates Corporation Belt tensioner with bottom wall of base juxtaposed pivot arm
US5924947A (en) * 1997-07-23 1999-07-20 Ford Global Technologies, Inc. Asymmetrically hydraulically damped drivebelt tensioner for automotive engine
US5935032A (en) 1998-06-02 1999-08-10 The Gates Corporation Tensioner with second pivot-arm for damping mechanism
US5938552A (en) * 1998-06-02 1999-08-17 The Gates Corporation Tensioner with damping shoe activated by compression spring
US6565468B2 (en) 1999-12-21 2003-05-20 The Gates Corporation Tensioner with damping mechanism
US6582332B2 (en) * 2000-01-12 2003-06-24 The Gates Corporation Damping mechanism for a tensioner
EP1250542B1 (de) * 2000-01-12 2004-09-22 The Gates Corporation Riemenspanner mit dämpfermechanismus
JP4050986B2 (ja) * 2000-10-03 2008-02-20 ザ ゲイツ コーポレイション モータ／ジェネレータと補機ベルト伝動システム
US7588507B2 (en) 2001-04-13 2009-09-15 Unitta Company Thin autotensioner
US6609988B1 (en) * 2001-05-24 2003-08-26 The Gates Corporation Asymmetric damping tensioner belt drive system
US7086373B2 (en) * 2002-11-01 2006-08-08 The Gates Corporation Damped accessory drive system including a motor/generator
US7004863B2 (en) 2002-05-15 2006-02-28 The Gates Corporation Damping mechanism
US7186196B2 (en) * 2002-07-18 2007-03-06 Dayco Products, Llc Belt tensioner with integral damping
US7090606B2 (en) * 2003-07-03 2006-08-15 The Gates Corporation Adjustable tensioner
US8337344B2 (en) * 2005-06-20 2012-12-25 Dayco Europe S.R.L. Asymetric damping belt tensioner
US8075433B2 (en) * 2005-06-28 2011-12-13 Dayco Products, Llc Belt tensioner with damping member
DE102005052453A1 (de) * 2005-11-03 2007-05-10 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen
DE102005060916A1 (de) * 2005-12-20 2007-06-28 Schaeffler Kg Spannvorrichtung für Zugmitteltriebe
DE102005060917A1 (de) * 2005-12-20 2007-06-28 Schaeffler Kg Spannvorrichtung für Zugmitteltriebe
DE102006004544A1 (de) * 2006-02-01 2007-08-02 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen oder eine Kette
DE102006004507A1 (de) * 2006-02-01 2007-08-02 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere für einen Riemen oder eine Kette
DE102006040672A1 (de) * 2006-08-30 2008-03-06 Schaeffler Kg Mechanische Spannsysteme für Zugmittelgetriebe
US7678002B2 (en) * 2006-08-31 2010-03-16 Dayco Products, Llc One-way clutched damper for automatic belt tensioner
DE102006059550A1 (de) * 2006-12-16 2008-06-19 Schaeffler Kg Spannvorrichtung für einen Zugmitteltrieb
DE102007031298A1 (de) * 2007-07-05 2009-01-08 Schaeffler Kg Dämpfungsvorrichtung eines mechanischen Spannsystems für einen Zugmitteltrieb
DE102007055664A1 (de) 2007-11-21 2009-05-28 Schaeffler Kg Werkstoffmischung aus Polyamid-Polyethylen für Spannsysteme
DE102008050384A1 (de) * 2008-10-02 2010-04-08 Schaeffler Kg Spann- und Dämpfungsvorrichtung für Zugmitteltriebe
WO2010037232A1 (en) 2008-10-02 2010-04-08 Litens Automotive Partnership Compact tensioner with sustainable damping
JP5276520B2 (ja) * 2008-10-10 2013-08-28 智和 石田 オートテンショナ
US8403785B2 (en) 2008-11-05 2013-03-26 Dayco Ip Holdings, Llc Clutched damper for a belt tensioner
DE102009020589A1 (de) * 2009-05-09 2010-11-11 Schaeffler Technologies Gmbh & Co. Kg Riemenspanneinheit
US20110015017A1 (en) * 2009-07-17 2011-01-20 Alexander Serkh Tensioner
US8157682B2 (en) * 2009-07-17 2012-04-17 The Gates Corporation Tensioner
DE102010019066A1 (de) * 2010-05-03 2011-11-03 Schaeffler Technologies Gmbh & Co. Kg Riemenspanner
US8439781B2 (en) 2010-06-22 2013-05-14 Dayco Ip Holdings, Llc Radial damping mechanism and use for belt tensioning
US8545352B2 (en) 2010-09-02 2013-10-01 Dayco Ip Holdings, Llc Tensioner with expanding spring for radial frictional asymmetric damping
US8617013B2 (en) 2010-09-02 2013-12-31 Dayco Ip Holdings, Llc Tensioner with expanding spring for radial frictional asymmetric damping
JP5627621B2 (ja) * 2011-04-28 2014-11-19 三ツ星ベルト株式会社 オートテンショナ
US20140287860A1 (en) * 2011-10-26 2014-09-25 Litens Automotive Partnership Tensioner with damping structure made from two components with no rotational play therebetween
US8932163B2 (en) * 2012-02-20 2015-01-13 Dayco Ip Holdings, Llc Belt tensioning device with variable spring factor
US9777806B2 (en) 2012-03-28 2017-10-03 Dayco Ip Holdings, Llc Sealed belt tensioning device
US9394977B2 (en) 2013-03-15 2016-07-19 Dayco Ip Holdings, Llc Tensioner with expanding spring for radial frictional asymmetric damping
CN105264267B (zh) * 2013-05-14 2018-04-27 利滕斯汽车合伙公司 具有改进阻尼的张紧器
CN203770558U (zh) * 2014-03-25 2014-08-13 宁波丰茂远东橡胶有限公司 一种发动机用大阻尼低衰减张紧器
US9982760B2 (en) * 2015-02-12 2018-05-29 Ningbo Fengmao Far-East Rubber Co., Ltd. Tensioner for engine with large and stable damping and minimum deflection of shaft
US9618099B2 (en) * 2015-07-13 2017-04-11 Gates Corporation Tensioner with secondary damping
JP6527550B2 (ja) * 2016-06-27 2019-06-05 三ツ星ベルト株式会社 補機駆動ベルトシステムに備わるオートテンショナ
US10883575B2 (en) 2018-01-03 2021-01-05 Gates Corporation Tensioner
BR112023017253A2 (pt) * 2021-02-26 2023-10-03 Dayco Ip Holdings Llc Tensor de correia de alta compensação com força de contrabalanceamento por mola de torção

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US4473362B1 (de) 1981-07-08 1991-07-09 Litens Automotive Inc
US4696663A (en) 1986-04-14 1987-09-29 Dyneer Corporation Belt tensioner
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005047265A1 (de) * 2005-10-01 2007-04-05 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs
DE102006023565A1 (de) * 2006-05-19 2007-11-22 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere einen Riemen oder eine Kette
DE102007015676A1 (de) * 2007-03-31 2008-10-02 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs
US8562467B2 (en) 2007-03-31 2013-10-22 Schaeffler Technologies AG & Co. KG Tensioning device of a belt and chain drive

Also Published As

Publication number Publication date
KR970046330A (ko) 1997-07-26
BR9606062A (pt) 2002-05-14
EP0780598B1 (de) 2000-11-02
CA2192422A1 (en) 1997-06-19
DE69610811D1 (de) 2000-12-07
KR100208042B1 (ko) 1999-07-15
ES2152497T3 (es) 2001-02-01
JPH09189348A (ja) 1997-07-22
US5632697A (en) 1997-05-27
CA2192422C (en) 2004-09-28
DE69610811T2 (de) 2001-06-07
ATE197341T1 (de) 2000-11-15
JP2854292B2 (ja) 1999-02-03

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